CN103032311A - Oil pump device - Google Patents
Oil pump device Download PDFInfo
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- CN103032311A CN103032311A CN 201210364076 CN201210364076A CN103032311A CN 103032311 A CN103032311 A CN 103032311A CN 201210364076 CN201210364076 CN 201210364076 CN 201210364076 A CN201210364076 A CN 201210364076A CN 103032311 A CN103032311 A CN 103032311A
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- Prior art keywords
- gear
- motor
- external gear
- internal gear
- rotor
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C2/00—Rotary-piston machines or pumps
- F04C2/08—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing
- F04C2/10—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of internal-axis type with the outer member having more teeth or tooth-equivalents, e.g. rollers, than the inner member
- F04C2/102—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of internal-axis type with the outer member having more teeth or tooth-equivalents, e.g. rollers, than the inner member the two members rotating simultaneously around their respective axes
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C15/00—Component parts, details or accessories of machines, pumps or pumping installations, not provided for in groups F04C2/00 - F04C14/00
- F04C15/0057—Driving elements, brakes, couplings, transmission specially adapted for machines or pumps
- F04C15/0061—Means for transmitting movement from the prime mover to driven parts of the pump, e.g. clutches, couplings, transmissions
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- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Rotary Pumps (AREA)
- Details And Applications Of Rotary Liquid Pumps (AREA)
Abstract
The invention provides an oil pump device. The pump housing is assembled with an inner wheel gear, an outer wheel gear and a motor part, and an unidirectional linking mechanism which conducts power transmission from the sleeve side to the inner wheel gear side between the outer periphery of the sleeve and the inner wheel gear, and cuts off power transmission of the opposite direction. The motor part is disposed at the outer periphery of the outer wheel gear in a manner of integrally retaining the rotor and the outer wheel gear and retaining the rotor to the pump housing. The motor part is assembled in that the rotor is rotated with respect to the stator through supplying current, and driving power is transmitted to the outer wheel gear. The inner and outer wheel gears are rotated with respect to each other through the driving power caused by the engine and the driving power caused by the motor part. Accordingly, pump function is generated.
Description
Technical field
The present invention relates to oil pump device.
Background technique
In the past, when the motor of vehicle moves, in order to supply with the oil be used to lubricated, the action of carrying out various mechanisms, control etc., assemble motor pump (for example, with reference to real flat 6-73387 communique, the Japanese kokai publication hei 9-25809 communique opened of Japan) in automatic transmission.
In addition, the known vehicle that is equipped with idling system, when vehicle temporarily stopped, this idling system temporarily stopped motor.In the vehicle that is equipped with such idling system, owing to temporarily stop (idle stop) of motor pump along with motor stops, so can't be to the clutch mechanism in the automatic transmission etc. for oil supply.
Therefore, except engine-driving in the past, also proposed when motor temporarily stops, can carrying out the oil pump device of the driving of motor, even the vehicle of idling system is installed, also can be to the clutch mechanism in the automatic transmission etc. for oil supply (for example, TOHKEMY 2010-71394 communique) when motor temporarily stops.
Yet, be following structure based on the oil pump device of TOHKEMY 2010-71394 communique, that is, utilize engine-driving, motor to drive and the internal gear driving, make the external gear rotation and the generation pumping action.That is, in aspect the relation of the inner peripheral surface of internal gear, the restriction that sets the space is remarkable in motor configurations.For the restriction that sets the space, also strict as the restriction in the spiral space of the coil of the formation of motor, the diameter of spiral, volume number also are restricted, and are difficult to consist of the large motor of output.
Therefore, according to the delivery volume of oil, need to supply with large electric current to motor and drive, thereby the problem that causes moyor to reduce is arranged.In addition, if the internal gear rotating speed uprises, then slip resistance becomes large, and the trend that has the loss of the driving force of motor to increase.
Summary of the invention
One of purpose of the present invention is to provide following oil pump device,, can guarantee the space that sets of motor that is, and the slip resistance can suppress motor and drive the time, and can suppress the loss of the driving force of motor.
Be characterised in that on the formation of the oil pump device of a mode of the present invention, in the pump assembling space of the pump case with suction port and exhaust port, be assembled with: internal gear, it has external tooth at outer circumferential face, and is embedded in the outer circumferential face of the output shaft of motor outward; External gear, it has internal tooth with the engagement of the external tooth of described internal gear at inner peripheral surface; And motor part, it possesses at the rotor that circumferentially sets a plurality of magnetic poles, with at the stator that circumferentially sets a plurality of coils, between the outer circumferential face of the output shaft of described motor and internal gear, be equipped with single-way linkage mechanism, this single-way linkage mechanism carries out from the transmission of power of the described internal gear side of output shaft side direction of described motor, and cut off from the transmission of power of the output shaft side of the described motor of described internal gear side direction, described motor part is equipped on the peripheral part of described external gear by following formation, this constitutes described rotor and described external gear is kept integratedly, and described stator remained in described pump case, described motor part constitutes, if it is supplied with electric current, then described rotor rotates with respect to described stator, thereby outside gear transmission driving force, make by the driving force that produced by the output shaft of described motor and driving force by described motor part generation that described internal gear is relative with external gear to be rotated, form pumping action.
Description of drawings
By the detailed description of preferred implementation of the present invention being carried out referring to accompanying drawing, further feature of the present invention, advantage can become clearer, and wherein, reference character represents key element of the present invention, wherein:
Fig. 1 is the sectional view of the oil pump device of expression embodiments of the present invention.
Fig. 2 is the sectional view that amplifies the oil pump device of expression embodiments of the present invention.
Fig. 3 is the plan view (the III-III line sectional view of Fig. 1) of internal gear, external gear and motor part of the oil pump device of expression embodiments of the present invention.
Fig. 4 is that expression is from the enlarged view of driving force state of inside gear transmission via single-way linkage mechanism of the sleeve of the oil pump device of embodiments of the present invention.
Fig. 5 is that the internal gear of oil pump device of expression embodiments of the present invention is with respect to the enlarged view of the state of sleeve idle running.
Fig. 6 is the stereogram that is illustrated in the hydrodynamic pressure bearing that consists of on the external gear of oil pump device of embodiments of the present invention.
Fig. 7 is the local amplification stereogram of the VII section of Fig. 6.
Fig. 8 is expression consists of the state of hydrodynamic pressure bearing as the variation 1 of the hydrodynamic pressure bearing of the oil pump device of embodiments of the present invention, in case side sectional view (the VIII-VIII line sectional view of Fig. 2).
Fig. 9 is expression consists of the state of hydrodynamic pressure bearing as the variation 1 of the hydrodynamic pressure bearing of the oil pump device of embodiments of the present invention, in case side plan view (the IX-IX line sectional view of Fig. 2).
Embodiment
According to Fig. 1～Fig. 7, the oil pump device of embodiments of the present invention is described.
As shown in Figure 1, oil pump device is assembled in the fluid torque converter 1 of automatic transmission.In oil pump device, pump case 10 is utilized bolt and is fixed in the shell (not shown) of automatic transmission.Pump case 10 constitutes utilizes bolt 9 to part the first housing 11 and 12 combinations of the second housing of cutting on the right side with Fig. 1 is left.Between the first housing 11 and the second housing 12, form pump assembling space 13.More specifically, pump assembling space 13 is by the first housing 11 and central parts the second housing 12 opposed internal faces forming with the first housing 11 opposed internal faces to the axial recessed assembling recess that forms and the second housing 12.
At the opposed internal face of the first housing 11 and the second housing 12, be formed with respectively suction port 15,17 and exhaust port 16,18.
At the central part of the second housing 12, dispose in the mode in the sleeve 2 of fluid torque converter 1 and to be formed with stator main shaft 5.
As shown in Figure 2, in the pump assembling space 13 of pump case 10, be assembled with motor pump and the integrated crescent gear pump 20 of motor-drive pump.When moving, motor drives above-mentioned motor pump.When temporarily stopping, motor drives above-mentioned motor-drive pump.This crescent gear pump 20 possesses motor part 30 and is assembled in the first housing 11 sides of pump assembling space 13.Said motor section 30 has internal gear 21, external gear 23, stator 31 and rotor 33.
As shown in Figure 3, internal gear 21 upwards has external tooth 21T in the week of outer circumferential face.Internal gear 21 has the center hole with the mode combination of the power of the sleeve 2 that can transmit via single-way linkage mechanism described later (mono-directional overrun clutch) 50 fluid torque converter 1.Above-mentioned center hole rotatably is intercalated in the outer circumferential face of the cartridge unit 51 of single-way linkage described later mechanism 50.
At the inner peripheral surface of internal gear 21, and be formed with many places pins containing space 21A with circumferential predetermined distance opening.Above-mentioned pin containing space 21A accommodates the set bar 52 of single-way linkage described later mechanism 50 and the position of spring 53.In the present embodiment, at the inner peripheral surface of internal gear 21, be formed with pin containing space 21A with 72 ° intervals.
In the example of present embodiment, as an example of 10 teeth example external tooth 21T is described.As shown in Figure 3, internal gear 21 rotates around Zi, and running shaft Zi is identical with the running shaft ZC of the sleeve 2 of fluid torque converter 1.Single-way linkage mechanism 50 as described later in detail.
As shown in Figure 3, external gear 23 around with the running shaft Zo rotation of the position of the rotating center of internal gear 21 eccentric (among Fig. 3, with the large small eccentricity of offset A).Week of the inner peripheral surface of external gear 23 upwards, be formed with the internal tooth 23T of a plurality of external tooth 21T engagements of a plurality of and internal gear 21.In the example of present embodiment, come internal tooth 23T is described take 11 teeth as example.Between the internal tooth 23T of the external tooth 21T of internal gear 21 and external gear 23, be formed with pocketed oil section 25.
As shown in Figure 2, (with the opposed face in bottom surface of the assembling recess of the first housing 11) is formed with the first annular convex 23a in a side of the external gear 23 of crescent gear pump 20.Bottom surface at the assembling recess of the first housing 11 is formed with the first annular recessed portion 11a, and this first annular recessed portion 11a embeds for above-mentioned first ring shape protuberance 23a and engages.Crescent gear pump 20 is assembled in the pump assembling space 13.Engage owing to the first annular convex 23a rotatably embeds with the first annular recessed portion 11a, thereby the external gear 23 of crescent gear pump 20 very stably is supported on the first housing 11.
Equally, the axial sides (with the opposed face of the internal face of the second housing 12) in the direction opposite with the first annular convex 23a of external gear 23 is formed with the second annular convex 23b.Internal face at the second housing 12 is formed with the second annular recessed portion 12a, and this second annular recessed portion 12a rotatably embeds for above-mentioned the second annular convex 23b and engages.Crescent gear pump 20 is assembled in the pump assembling space 13, engage owing to the second annular convex 23b rotatably embeds with the second annular recessed portion 12a, thereby the external gear 23 of crescent gear pump 20 very stably is supported on the second housing 12.
Above-mentioned the first annular convex 23a and the first annular recessed portion 11a, the second annular convex 23b and the second annular recessed portion 12a are in order to implement from the swivel bearing radially of external gear 23 and consist of.That is, as shown in Figure 2, at the outer circumferential face of above-mentioned external gear 23, be provided with the rotor 33 of motor part 30 described later.And dispose to consist of in the mode of leaving to radial outside from above-mentioned rotor 33 stator 31 is arranged.Therefore, by consisting of the first annular convex 23a and the first annular recessed portion 11a, the second annular convex 23b and the second annular recessed portion 12a, come from 23 rotations of radial support external gear.
In addition, such as Fig. 2, Fig. 6, shown in Figure 7, on the first slip surface 60 that the first annular recessed portion 11a of the first annular convex 23a that is formed in external gear 23 and the first housing 11 slides, consist of hydrodynamic pressure bearing, namely, utilize relative sliding motion and make the lubricating fluid film produce kinetic pressure, thereby supporting load radially.
Specifically, such as Fig. 6, shown in Figure 7, on the complete cycle of the outer circumferential face of the first annular convex 23a of external gear 23, be formed with adjacently the groove 62 of a plurality of V fonts.Herein, the groove 62 of V font forms, and paddy section 64 is disposed at the rear side of the sense of rotation of external gear 23.Groove 62 mobile oil along this V font gather in paddy section 64, and produce kinetic pressure.
Equally, such as Fig. 2, Fig. 6, shown in Figure 7, on the second slip surface 70 that the second annular recessed portion 12a of the second annular convex 23b that is formed in external gear 23 and the second housing 12 slides, consist of hydrodynamic pressure bearing, namely, utilize relative sliding motion and make the lubricating fluid film produce kinetic pressure, thereby supporting load radially.
Specifically, such as Fig. 6, shown in Figure 7, on the complete cycle of the outer circumferential face of the second annular convex 23b of external gear 23, be formed with adjacently the groove 72 of a plurality of V fonts.Herein, the groove 72 of V font forms, and paddy section 74 is disposed at the rear side of the sense of rotation of external gear 23.Groove 72 mobile oil along this V font gather in paddy section 74, and produce dynamic pressure.
Such as Fig. 2 and shown in Figure 3, motor part 30 is assembled in the peripheral part (radial outside) of external gear 23 in pump assembling space 13, and possesses stator 31 and rotor 33.
The stator 31 of motor part 30 possesses core part 32a and a plurality of coil 32b.Above-mentioned a plurality of coil 32b is installed on circumferential a plurality of coil assembly departments of the inner peripheral surface that is formed at above-mentioned core part 32a, and to dispose with the opposed mode of the outer circumferential face of rotor 33.In description of the present embodiment, to respect to the number of magnetic poles of 8 utmost points of rotor 33 and the example with stator 31 of 12 coil 32b describe.
The magnitude of interference that produces with the bolt 9 by fastening the first housing 11 and the second housing 12 is fixed in stator 31 between the first housing 11 and the second housing 12.Plurality of positions (with the corresponding position of a plurality of coil 32b) at the outer circumferential face of the core part 32a of stator 31 is formed with circular-arc notch recesses 31a.When utilizing a plurality of bolt 9 fastening the first housings 11 and the second housing 12, the screw section of these a plurality of bolts 9 connects notch recesses 31a, and the screw section of a plurality of bolt 9 engages with a plurality of notch recesses 31a.Utilize the screw section of a plurality of bolts 9 and the power that engages of a plurality of notch recesses 31a, stator 31 can't be rotated.
That is, when utilizing a plurality of bolt 9 fastening the first housings 11 and the second housing 12, can carry out the fixing of stator 31.Connect notch recesses 31a by the screw section that makes a plurality of bolts 9, can suppress to comprise that the diameter dimension of integral body of the first housing 11 and the second housing 12 is excessive, thereby can guarantee easily the configuration space of motor part 30.
The rotor 33 of motor part 30 circumferentially alternately is being arranged with a plurality of S utmost points corresponding with coil 32b and the magnet of the N utmost point.But fix to the interior perimembranous of above-mentioned rotor 33 and the outer circumferential face transferring power of external gear 23.Thus, rotor 33 and the rotation of external gear 23 one.In description of the present embodiment, the example with the rotor 33 that has 8 number of magnetic poles (the N utmost point and the S utmost point add up to) with respect to 12 coil 32b of stator 31 describes.
Next, in conjunction with Fig. 3 ~ Fig. 5, the structure of single-way linkage mechanism 50 is described.
This single-way linkage mechanism 50 constitutes the output shaft that the sleeve 2(that is configured in fluid torque converter 1 is equivalent to motor of the present invention) outer circumferential face and internal gear 21 between.This single-way linkage mechanism 50 carries out cutting off from the mechanism of the transmission of power of internal gear 21 lateral sleeves 2 sides from the transmission of power of sleeve 2 side direction internal gears 21 sides.
This single-way linkage mechanism 50 has cartridge unit 51, set bar 52 and spring 53.
But cartridge unit 51 has the center hole of sleeve 2 combinations of inner peripheral surface transferring power ground and fluid torque converter 1.In addition, the outer circumferential face of cartridge unit 51 and with the opposed position of pin containing space 21A of the inner peripheral surface of internal gear 21 on along circumferentially being formed with a plurality of interlock groove 51A with predetermined distance, this interlock groove 51A can engage, separate with set bar 52.In the present embodiment, be formed with interlock groove 51A along circumferential interval with 72 °.
For interlock groove 51A, on the face of a sense of rotation (be clockwise direction in the example of Fig. 4), be formed with the plane of inclination 51C towards the outer circumferential face inclination of cartridge unit 51 from the bottom surface 51D of interlock groove 51A.In addition, on the face of another sense of rotation (being counterclockwise in the example of Fig. 4), be formed with vertical surface 51B with the bottom surface 51D from interlock groove 51A towards the mode of the outer circumferential face of cartridge unit 51.
In the pin containing space 21A of internal gear 21, contain spring 53 and set bar 52 as force application mechanism.Utilize spring 53 so that it comes above-mentioned set bar 52 application of forces to the outstanding mode of the radially inner side of internal gear 21.In other words, utilize spring 53, towards the running shaft ZC(of sleeve 2 namely, the running shaft Zi of internal gear 21) direction to set bar 52 application of forces.Set bar 52 can the direction from pin containing space 21A to running shaft ZC be given prominence to, and can be housed in the pin containing space 21A.
According to above-mentioned formation, as shown in Figure 4, in the situation of clockwise direction (the Ri direction of Fig. 4) rotation, engage with the vertical surface 51B of interlock groove 51A by making set bar 52 with respect to internal gear 21 at sleeve 2, make sleeve 2 and the rotation of internal gear 21 one.That is, internal gear 21 is subject to rotating from the transmission of power of the sleeve 2 of fluid torque converter 1, accompanies therewith, and external gear 23 is followed rotation, thereby produces pumping action.
As shown in Figure 5, at external gear 23 with respect to internal gear 21 and in the situation of clockwise direction (the Ro direction of Fig. 5) rotation, internal gear 21 is followed rotation to clockwise direction therewith together, thereby produce pumping action.At this moment, set bar 52 can overcome the active force of spring 53 and move at the plane of inclination 51C of interlock groove 51A, and can move to the outer circumferential face of cartridge unit 51, thereby internal gear 21 is with respect to sleeve 2 idle running.
According to above formation, in the situation of sleeve 2 rotation of fluid torque converter 1, even do not make motor part 30 rotations, mechanically drive internal gear 21 rotations by engaging single-way linkage mechanism 50, also can make external gear 23 follow rotation along with the rotation of internal gear 21.Therefore, in the situation of sleeve 2 rotation of fluid torque converter 1, crescent gear pump 20 is as mechanically being driven the motor pump that rotates by sleeve 2 and moving.
Rotation at the sleeve 2 of fluid torque converter 1 stops in the situation of (idle stop), and not shown motor control mechanism is in due course, and each is switched on to a plurality of coil 32b of stator 31, and coming electric-driven rotor 33(is external gear 23) rotation.And internal gear 21 is followed rotation along with the driving rotation of external gear 23.At this moment, utilize single-way linkage mechanism 50, make internal gear 21 with respect to sleeve 2 idle running.Therefore, stop in the situation of (idle stop) in the rotation of the sleeve 2 of fluid torque converter 1, crescent gear pump 20 is as being driven the motor-drive pump of rotation by not shown motor control mechanism electricity and moving.
In addition, even in the situation of sleeve 2 rotations, also can make it to rotate than the fireballing speed of the mechanical type rotating that is caused by sleeve 2 by electric-driven rotor 33, at this moment, motor pump and motor-drive pump interoperation.
Like this, according to the oil pump device of present embodiment, motor part 30 is equipped on the peripheral part of external gear 23 by following formation, namely, rotor 33 and external gear 23 are kept integratedly and stator 31 is remained in pump case 10.Motor part 30 constitutes, if it is supplied with electric current, then rotor 33 is with respect to stator 31 rotations, thus to external gear 23 transmission of drive force.
Herein, for the internal tooth 23T of the external tooth 21T of internal gear 21 and external gear 23, the number of teeth of external gear 23 is more.Therefore, for the amount of revolving the oil of discharging that turns around, external gear 23 is than internal gear more than 21.In other words, if discharge identical oil mass, then drive external gear 23 and compare driving internal gear 21, rotating speed is little.That is, by being made as low rotation, the slip resistance in the time of can suppressing the driving of motor part 30.Its result can suppress the loss of the driving force of motor part 30, thereby can improve moyor.Motor part 30 is equipped on the peripheral part of external gear 23.Compare with the interior perimembranous of internal gear 21, the peripheral part of external gear 23 can be guaranteed the space that sets of larger motor part 30.Therefore, the spiral space of coil 32b, the diameter of spiral, volume number etc. are difficult to be restricted, thereby can set the motor part 30 of high output.In addition, because the space that sets that can guarantee larger motor part 30, thereby the degrees of freedom of design can be improved.
Maintain integratedly the rotor 33 of motor part 30 at the peripheral part of external gear 23, stator 31 remains in pump case 10 accordingly with above-mentioned rotor 33.The equipping position that needs to consider rotor 33, stator 31 carries out the supporting radially of external gear 23.By following formation, the formation that namely, the first annular convex 23a of external gear 23 engages with the first annular recessed portion 11a of the first housing 11 and the second annular convex 23b engages with the second annular recessed portion 12a of the second housing 12, come external gear wheel 23 to support, make its relatively pump case 10 rotations.Thus, can be easily set motor part 30 at the peripheral part of external gear 23, and can easily carry out the swivel bearing radially of external gear 23.
On the complete cycle of the outer circumferential face of the first annular convex 23a of external gear 23 (the first slip surface 60), be formed with the groove 62 of the V font that consists of as hydrodynamic pressure bearing.Equally, on the complete cycle of the outer circumferential face of the second annular convex 23b of external gear 23 (the second slip surface 70), be formed with the groove 72 of the V font that consists of as hydrodynamic pressure bearing.Therefore, produce kinetic pressure by make the lubricating fluid film at the position as sliding bearing, can prevent the sintering at the position of the first slip surface 60 and the second slip surface 70.In addition, owing to can utilize the groove 62 of the V font of hydrodynamic pressure bearing, 72 formation to obtain higher rigidity, thus can improve reliability, and can enlarge the design application area of oil pump device.
More than, embodiments of the present invention are illustrated, but oil pump device of the present invention is not limited to present embodiment, can implement in other various mode.
For example, the number of teeth of external gear and internal gear is not limited to the number of teeth that illustrates in the present embodiment, and can use the various numbers of teeth.
In addition, the quantity of the coil of the number of magnetic poles of rotor, stator can be made as various quantity.
In addition, outside oil pump device of the present invention for example can be used as the employed various oil pump devices of vehicle, also can be used as the suction of carrying out various fluids and the various mechanical pumps of discharge and utilize.
In addition, the formation of the represented hydrodynamic pressure bearing of above-mentioned mode of execution is not limited to the groove 62,72 of V font.Fig. 8 and Fig. 9 represent modified embodiment of the present embodiment 1.
For example, such as Fig. 2, shown in Figure 8, also can be at the inner peripheral surface of the first annular recessed portion 11a of the first housing 11 along the groove 80 that circumferentially consists of a plurality of wedge-likes.The groove 80 of this wedge-like is formed with the plane of inclination 82 that the front side of the sense of rotation of gear 23 outward seals gradually, by gather oil between this plane of inclination 82 and external gear 23, produces kinetic pressure.
Equally, such as Fig. 2, shown in Figure 9, also can be at the inner peripheral surface of the second annular recessed portion 12a of the second housing 12 along the groove 90 that circumferentially consists of a plurality of wedge-likes.The groove 90 of this wedge-like is formed with the plane of inclination 92 that the front side of the sense of rotation of gear 23 outward seals gradually, by gather oil between this plane of inclination 92 and external gear 23, produces kinetic pressure.
The present invention can provide following oil pump device by adopting mechanism of above-mentioned each invention,, can guarantee the space that sets of motor that is, and the slip resistance can suppress motor and drive the time, thereby can suppress the loss of the driving force of motor.
Claims (2)
1. an oil pump device is characterized in that, is assembled with in the pump assembling space of the pump case with suction port and exhaust port:
Internal gear, it has external tooth at outer circumferential face, and is embedded in the outer circumferential face of the output shaft of motor outward;
External gear, it has internal tooth with the engagement of the external tooth of described internal gear at inner peripheral surface; And
Motor part, it possess the rotor that circumferentially sets a plurality of magnetic poles, with at the stator that circumferentially sets a plurality of coils,
Between the outer circumferential face of the output shaft of described motor and internal gear, be equipped with single-way linkage mechanism, this single-way linkage mechanism carries out from the transmission of power of the described internal gear side of output shaft side direction of described motor and cuts off from the transmission of power of the output shaft side of the described motor of described internal gear side direction
Described motor part is equipped on the peripheral part of described external gear by following formation, and this constitutes described rotor and described external gear are kept integratedly, and described stator is remained in described pump case,
Described motor part constitutes, if it is supplied with electric current, then described rotor rotates with respect to described stator, thus outside gear transmission driving force,
Make by the driving force that produced by the output shaft of described motor and driving force by described motor part generation that described internal gear is relative with external gear to be rotated, form pumping action.
2. oil pump device according to claim 1 is characterized in that,
On at least one side in the axial sides of described external gear, form outstanding vertically annular convex,
On the pump case corresponding with described annular convex, form the annular recessed portion of the engaging for described annular convex embeds,
By described annular convex is engaged with annular recessed portion, come described external gear is supported, it can relatively described pump case be rotated.
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2011-212255 | 2011-09-28 | ||
| JP2011212255A JP2013072371A (en) | 2011-09-28 | 2011-09-28 | Oil pump device |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN103032311A true CN103032311A (en) | 2013-04-10 |
Family
ID=46939637
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN 201210364076 Pending CN103032311A (en) | 2011-09-28 | 2012-09-26 | Oil pump device |
Country Status (2)
| Country | Link |
|---|---|
| JP (1) | JP2013072371A (en) |
| CN (1) | CN103032311A (en) |
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| CN108138769A (en) * | 2015-09-24 | 2018-06-08 | Ntn株式会社 | oil pump driving device |
| CN108368846A (en) * | 2015-12-24 | 2018-08-03 | Ntn株式会社 | Oil pump driving device |
| CN111417782A (en) * | 2017-12-27 | 2020-07-14 | Ｋｙｂ株式会社 | Electro-hydraulic actuator |
| CN111727322A (en) * | 2018-05-15 | 2020-09-29 | 舍弗勒技术股份两合公司 | Integrated eccentric motor and pump assembly |
| CN112039306A (en) * | 2019-06-04 | 2020-12-04 | 本田技研工业株式会社 | Electric oil pump |
Families Citing this family (4)
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| KR101876071B1 (en) * | 2016-10-31 | 2018-07-06 | 현대 파워텍 주식회사 | Connecting structure of torque convertor hub and oil pump gear for an automatic transmission |
| KR102261825B1 (en) * | 2018-12-12 | 2021-06-08 | 현대트랜시스 주식회사 | Torque converter and oil pump connecting device for automatic transmission |
| CN114846259A (en) * | 2019-12-17 | 2022-08-02 | 伊格尔工业股份有限公司 | Sliding component |
| US11913449B2 (en) | 2019-12-17 | 2024-02-27 | Eagle Industry Co., Ltd. | Sliding component |
Family Cites Families (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2005273648A (en) * | 2004-02-23 | 2005-10-06 | Aisin Seiki Co Ltd | Electric pump |
| JP4084351B2 (en) * | 2004-12-24 | 2008-04-30 | 株式会社日立製作所 | Motor-integrated internal gear pump and electronic equipment |
| JP4237731B2 (en) * | 2005-05-31 | 2009-03-11 | 株式会社日立製作所 | Motor-integrated internal gear pump, method for manufacturing the same, and electronic device |
| US8182235B2 (en) * | 2008-11-25 | 2012-05-22 | Toyota Motor Engineering & Manufacturing North America, Inc. | Multi-drive fluid pump |
-
2011
- 2011-09-28 JP JP2011212255A patent/JP2013072371A/en active Pending
-
2012
- 2012-09-26 CN CN 201210364076 patent/CN103032311A/en active Pending
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| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN108138769A (en) * | 2015-09-24 | 2018-06-08 | Ntn株式会社 | oil pump driving device |
| EP3354898A4 (en) * | 2015-09-24 | 2018-10-10 | NTN Corporation | Oil pump driving device |
| CN108138769B (en) * | 2015-09-24 | 2020-04-17 | Ntn株式会社 | Oil pump driving device |
| US11204033B2 (en) | 2015-09-24 | 2021-12-21 | Ntn Corporation | Oil pump driving device |
| CN108368846A (en) * | 2015-12-24 | 2018-08-03 | Ntn株式会社 | Oil pump driving device |
| US10683926B2 (en) | 2015-12-24 | 2020-06-16 | Ntn Corporation | Oil pump driving device |
| CN108368846B (en) * | 2015-12-24 | 2021-04-09 | Ntn株式会社 | Oil pump driving device |
| CN111417782A (en) * | 2017-12-27 | 2020-07-14 | Ｋｙｂ株式会社 | Electro-hydraulic actuator |
| CN111727322A (en) * | 2018-05-15 | 2020-09-29 | 舍弗勒技术股份两合公司 | Integrated eccentric motor and pump assembly |
| CN112039306A (en) * | 2019-06-04 | 2020-12-04 | 本田技研工业株式会社 | Electric oil pump |
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| Publication number | Publication date |
|---|---|
| JP2013072371A (en) | 2013-04-22 |
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Application publication date: 20130410 |